Transfer gear case



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TRANSFER GEAR CASE Feb. 11, 1947.

Filed May 23, 1944 5 Sheets-Sheet 5 INVENTORS CHEL .D. PETE/e60 TTORNE Y6 Patented Feb. 11, 1947 TRANSFER GEAR CASE Carl D. Peterson and Elmer J. Earth, Toledo, @hio; said Barth assignor to Dana Corporation, Toledo, Ohio, a corporation of Virginia Application May 23,1944, Serial No. 536,918

This invention has for its object an auxiliary gear and gear case for use in connection with or attachment to a main gear box, and more specifically has for its object an auxiliary or transfer gear case, by which the power coming from a motor of a vehicle through the main change-speed gear box,. is readily applied to both the front and the rear axles of the vehicle, or only to one of said axles, as the rear axle at the will of the driver. It also has for its object an auxiliary gear case or box construction and the arrangement of gearing therein which results in an extremely compact unit to supply the power, through propeller shafts, to both the front and rear axles with provision for choice as to whether one axle only, as the rear axle, is to be power driven, and also providing for two gear ratios to one or both axles. t

The invention consists in the novel features and in the combinations and constructions hereinafter set forth and claimed.

In describing this invention, reference is had to the accompanying drawings in which like characters designate corresponding parts in all the views.

Figure 1 is a fragmentary perspective view of a front and rear wheel axle drive, the engine and the main gear box being omitted.

Figure 2 is an enlarged sectional view taken approximately on the plane of line 2-2, Figure 4.

Figure 3 is an end elevation looking to the left I in Figure 2.

Figure 4 is an opposite end elevation from that seen in Figure 3.

Figure 5 is a view similar to Figure 2 of a modified arrangement of the gearing within the gear box and of the brake.

Figures 6 and 7 are views looking to the left and right respectively in Figure 5.

This gearing is for supplying a driving force to the front and rear axles of a vehicle by applying a transfer gear to the main change-speed gearing and. for driving'the axles through a plurality, preferably two gear ratios, in. addition to the gear changes provided. by the change-speed gearing in the main gear box, and for. connecting or disconnecting one of the axles, as the front axle, and the power drive at will. It further has for its object a particularly compact arrangement of the transfer gear case ad the gears therein by which it is compactly applied to amain gear box.

In Figure 1, the transfer case is. shown as. em-

bodied in a front and rear'drive axle unit applied r 2 Claims. (Cl. 74-343) to the frame or body carrying the engine, changespeed transmission gear, vehicle springs, etc.

I designates the transfer case; 2 and 3 propeller shafts to the rear and the front axles respectively from the two output shafts within the transfer gear box; 4 a face plate on the body of the transfer case for attachment to the main gear box, in which is located a conventional change-speed transmission gearing with, for instance, three speeds forward and reverse, the input shaft of the main gear box being connected to the engine supported on the chassis in any well known manner. 5 and 6 are housings for differential gears through which the power is transmitted to. the front and rear ground Wheels, the rear wheels being mounted on spindles l on the axle shaft section and the front wheels on spindles 8 capable of being turned through knuckle mechanism to steer the vehicle, all as is well understood. A fragmentary portion of the main gear box is shown in broken lines at 9 (Figure 2).

The transfer case i includes a main body having the face plate or flange i at one side and the major portion of the body extending laterally therefrom. The part of the body on which the face plate is provided being formed with an opening I ilin which is mounted a bearing for the output shaft of the change-speed gearing, this output shaft being the input shaft E! (Figure 2) of the transfer gearing within the transfer box. I?! and i3 designate output shafts mounted in axial al'i'nement in suitable bearings in the transfer case i and located in a general horizontal direction laterally from the portion of the case in which the input shaft I l is located, the output shaft l2 being connected by the propeller shaft 2 to the rear axle shaft through the differential gearing 5. The output shaft !3 is connected to the propeller shaft 3, which drives the front wheels, mounted" on the spindles 3. The transfer case is a one-piece unitary structure with two exceptions hereinafter pointed out, but with bearings for the various shafts located in opposing walls of the integral portion of the case. The two exceptions are: (A) that the bottom portion of the case, which serves as an oil sump is provided with a removable pan It, and (B) that the lateral portion is provided with a removable cover l5 alined with the shaft l l.

The input shaft H is connected toone of the output shafts, as the shaft 52, which drives the rear axle, through two trains of gears to transmit different gear ratios; The output shaft [3 which drives the front axle may be connected and disconnected at will from the shaft l2 by a suitable jaw clutch 6. The gear ratios may be whatever are required to give the desired performance of the particular vehicle in which the transfer case is utilized. One or more gear ratios may be provided to give at least one high and one low speed range.

In the form shown in Figure 2, one train of gears includes the drive gear I! on the input shaft, a driven gear If: on the output shaft 12 and an intermediary gear mounted on a suitable spindle 2| in the body of the transfer case i, the gear it being rotatably mounted on the output shaft l2 and connectable thereto by a clutch gear 22 keyed or splined on the output shaft l2 and forming part of the reduction gear train. The reduction gear train also includes the clutch gear 22 which maybe meshed with an intermediary gear 23 on the spindle 2i and rotatable as a unit with the gear 20. The clutch gear 22 is shiftable from the position in which it is in mesh with the gear 23 into an intermediate position and from the intermediate position to clutch engaged position with the gear 89. The gear i9 is provided with external clutch teeth 24 for coacting with splines in the bore of the gear 22. When the clutch gear 22 is in position to clutch the gear 9 to the shaft l2, the drive is through a hi h speed gear ratio between the input shaft H and the output shaft I2. If the clutch H3 is shifted into engaged position, both the front and rear axles will be actuated through the high speed gear ratio. If the clutch I6 is disengaged only the rear axle will be driven by power. When the clutch gear 22 is in position shown in Figure 2, whereit is engaged with the intermediary gear 23, the rear axle will be driven through the output shaft i2 from the drive gear 11 through the gears 20, 23 and 22. The other output shaft l3 driving the front wheel will also be so actuated, if the clutch i6 is engaged.

A suitable vehicle brake is carried on the output shaft 52, which drives the propeller shaft 2 to the rear axle. As seen in Figure 2, this includes a brake drum 25 mounted directly on the output shaft 12 outside the transfer case, with which coacts a brake band 25. The output shaft 12 may also drive a suitable speedometer mechanism through the spiral gearing 21, 28. The mounting for the brake drum 25 is provided with a coupling at 29 for connection to one section of the universal joint at the front end of the propeller shaft 2. The output shaft I3 is also provided with one section of a universal joint 38 (Figure 1) for the propeller shaft 3.

The clutch l6 and clutch gear 22 are shiftable by suitable forks 3! and 32 connected to shift rods 33 and 34, which in turn are operated by hand levers 35 and 3B, the shift rods being located in the body of the transfer case l directly above output shafts l2, l3 and the levers being mounted in a suitable bracket 31 on the integral top side of the transfer gear case and having arms extending downwardly in front of the front side of the transfer gear case at one side of the face plate A, where they interlock at 38 and 39 in suitable notches in the front ends of the shift rods 33, 34 which extend through the front side of the transfer gear case i The brake band 25 is applied in any well known manner by brake band mechanism 42 mounted on the rear wall of th transfer gear case and operable to contract the brake band on the brake drum. The brake mechanism is operated through a suitable lever 43 for connection to a brake pedal remote from the gear case. I

In the form shown in Figures 5, 6 and 7, the transfer case is an integral structure with the top open and provided with a removable cap 45. The bottom, however, is integral with the side and end Walls and is provided with a drain plug 46 for the oil within the lower part of the transfer gear case, which acts as a sump.

In the construction shown in Figure 5, the transfer gearing and the brake arrangement and levers are slightly modified from the corresponding structures shown in Figures 2, 3 and 4 and also an additional output shaft provided.

In Figure 5, the trains of gears between the input shaft H and the output shafts I2, l3 are through a high speed gear ratio as follows: drive gear t? on the input shaft ll, driven gear 48 on the output shaft I2, intermediary gear 50 meshing with the gears 49, 48, when the gear 49 is clutched to act as a unit with the gear 41. The gear 59 is mounted on a spindle 5! mounted in the gear box. In this construction, the brake drum 25 is mounted on a separate shaft 52 mounted in the case in line with the input shaft 5! and connected or clutched thereto through a clutch 53 operable to clutch an extended hub or sleeve on th drive gear 47 to the hub of the gear as when shifted in one direction, as to the right. The gear ts is a unit with the brake shaft 52. The low speed gear ratio is through the gear 54 on the spindle 5i and meshing with the drive gear 41. The gear 54 is clutchable to the gear 50 to act as a unit therewith by a shiftable clutch section 55. The gear 49 of the high speed gear ratio is clutched to the alined drive gear 41 through a clutch section 53 shiftable to the right from the position shown in Figure 5 to clutch the gear 49 to the gear 41. The two clutches 53 and 55 are ,shiftable as a unit by one fork 56. When the drive is through the low speed gear ratio, the clutch 55 is shifted to clutch the intermediary gear 5Q. When the drive is through the low speed gear ratio or through the intermediary gears 54 and 5B acting as a unit, the brake shaft 52 is unclutched from the drive gear. When the brake shaft 52 is unclutched from the drive shaft H, the brake is still effective when the drive is from the drive shaft H through gears 41, 54, Ell

and 48, since the gear as on the brake shaft is in mesh with the gear 56. The fork for shifting the clutch 15 between the output shafts l2 and I3 and the double fork 56 are operated from two hand levers 5'! and 58, these being mounted on concentric inner and outer shafts E8 and 60 extending transversely of the gear casing l and mounted in suitable bracket Bl thereon. These levers are located on the side of the casing nearest the input shaft instead of the side nearest the output shaft i, as in Figures 1, 2 and 3.

A third power take off shaft may be provided here shown as driven directly from the input shaft I i. In Figure 2, this third power take off is shown in dot-dash lines. H designates the power take ofi shaft. It may be clutched to the gear ll on the input shaft I l by a normally open clutch 5B slidably splined on a collar 69 on the shaft H and shiftable into and out of engagement with clutch teeth Ill on the hub of the drive gear H, the shaft i I being mounted in alinement with the shaft 1 i. The shaft I l is mounted in a suitable bearing, not shown, provided in a plate substituted for the cover i5, in a manner similar to that in which the bearing for the shaft 52 in Figure 5 is mounted. The clutch B8 is operated by a suitable shift rod H to which is connected an additional shift lever. Thus, the shaft H a may be actuated at any time the clutch 68 is shifted into clutching engagement with the shaft ll through the clutch teeth 19 on the gear I! and hence this power take off may be used at any time when the vehicle is in motion or when the output shafts l2, 13 are unclutched.

In the form shown in Figure 5, the brake shaft 52 is used as a third power take off, and for this purpose the brake drum or the hub thereof is provided with one section of a coupling 12 for connection to another section on a propeller shaft for power take off purposes. As the shaft 52 is clutched to the shaft ll through the clutch 53 when shifted to the right, power may be taken ofi directly from the shaft 1 I and indirectly from the shaft II, when the clutch 55 is shifted to the left.

The inner and outer concentric shafts 59 and 60 are connected by rock arms 62, 63 which coact with arms 64 and 65, which in turn coact with the shift rods 56, 57. The shift rod 66 operates the fork 56 and hence the clutches 53, 55 and the arm 65 operates the clutch 16 in Figure 5 between the output shafts I2 and [3, the arm 64 being double and pivoted between its ends.

The brake mechanism is substantially the same as that shown in Figure 2 with the exception of the location of the brake drum.

What we claim is:

1. An auxiliary transfer gearing including a case for attachment to a main, change-speed gear box, an input shaft journalled in the case, this being the output shaft of the gearing in the main gear box, a pair of axially alined output shafts journalled in the case, a third shaft journalled in the case in axial alinement with the input shaft, gears on the input and on the third shafts and rotatable therewith respectively, a gear on one of the output shafts, a pair of intermediary gears, one meshing with the gear on the input shaft and the other with the gears on the third and the output shafts, a clutch shiftable in one direction to clutch the input and the third shafts together and thus effect a drive through one train of gears, a second clutch shiftable in the opposite direction to clutch the intermediary gear which meshes with the gear on the input shaft to the other intermediary gear, means for shifting said clutches in unison, whereby the clutches are shiftable alternately into engaged position from idle position, and a clutch operable to clutch the output shafts directly together.

2. An auxiliary transfer gearing including a case for attachment to a main, change-speed gear box, an input shaft journalled in the case, this being the output shaft of the gearing in the main gear box, a pair of axially alined output shafts journalled, in the case, a third shaft journalled in the case in axial alinement with the input shaft, gears on the input and on the third shafts and rotatable therewith respectively, a gear on one of the output shafts, a pair of intermediary gears, one meshing with the gear on the input shaft and the other with the gears on the third and the output shafts, a clutch shiftable in one direction to clutch the input and the third shafts to gether and thus effect a drive through one train of gears, a second clutch shiftable in the opposite direction to clutch the intermediary gear which meshes with the gear on the input shaft to the other intermediary gear, means for shifting said clutches in unison, whereby the clutches are shiftable alternately into engaged position from idle position, a clutch operable to clutch the output shafts directly together, and

a brake including a drum mounted on the third shaft outside of the casing.

CARL D. PETERSON. ELMER J. BARTH.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS TM-10-1513 (publication), May 15, 1942.

Automotive Power Transmission Units, TM-lO-- 585 (publication), April 10, 1941. 

